WO2012043254A1 - タービン - Google Patents
タービン Download PDFInfo
- Publication number
- WO2012043254A1 WO2012043254A1 PCT/JP2011/071101 JP2011071101W WO2012043254A1 WO 2012043254 A1 WO2012043254 A1 WO 2012043254A1 JP 2011071101 W JP2011071101 W JP 2011071101W WO 2012043254 A1 WO2012043254 A1 WO 2012043254A1
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- WIPO (PCT)
- Prior art keywords
- dead water
- cavity
- blade
- axial direction
- vortex
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/20—Specially-shaped blade tips to seal space between tips and stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
- F01D5/225—Blade-to-blade connections, e.g. for damping vibrations by shrouding
Definitions
- the present invention relates to a turbine used in, for example, a power plant, a chemical plant, a gas plant, a steel mill, a ship, and the like.
- a turbine used in, for example, a power plant, a chemical plant, a gas plant, a steel mill, a ship, and the like.
- a casing As a kind of steam turbine, a casing, a shaft body (rotor) rotatably provided inside the casing, a stationary blade fixedly disposed on an inner peripheral portion of the casing, and a downstream side of the stationary blade
- An impulse turbine is one in which a moving blade rotates only by an impact force received from steam.
- the stationary blade has a nozzle shape, and the steam that has passed through the stationary blade is injected to the moving blade, and the moving blade rotates only by the impact force received from the steam.
- the reaction turbine has the same shape as the moving blade, and the moving blade is affected by the impact force received from the steam passing through the stationary blade and the reaction force against the expansion of the steam generated when passing through the moving blade. Is what rotates.
- a gap having a predetermined width is formed in the radial direction between the tip portion of the rotor blade and the casing, and also between the tip portion of the stationary blade and the shaft body.
- a gap having a predetermined width is formed in the direction.
- a part of the steam flowing in the axial direction of the shaft body leaks to the downstream side through the clearance between the tip portions of the rotor blades and the stationary blades.
- the steam leaking downstream from the gap between the moving blade and the casing does not give impact force or reaction force to the moving blade, so that the driving blade is rotated regardless of whether it is an impulse turbine or a reaction turbine. Little contribution as power.
- the steam leaking downstream from the gap between the stationary blade and the shaft body does not change its speed and does not expand even if it exceeds the stationary blade, so regardless of whether it is an impulse turbine or a reaction turbine, It hardly contributes as a driving force for rotating the moving blade on the downstream side. Therefore, in order to improve the performance of the steam turbine, it is important to reduce the amount of steam leakage in the gap between the tip portions of the moving blades and the stationary blades.
- seal fins are conventionally used as a means for preventing steam from leaking from the gaps at the tips of the rotor blades and stationary blades.
- this seal fin is used at the tip of a moving blade, it is provided so as to protrude from one of the moving blade and the casing and to form a minute gap between the other.
- the corner of the casing is formed in a curved shape in a cross section along the axial direction so that stress concentration caused by the thermal expansion of the casing does not occur in the corner formed by the wall surface of the casing.
- the curved shape of the casing corner is generally an arc shape having a radius of about 1 mm.
- the present invention has been made in consideration of such circumstances, and an object of the present invention is to provide a high-performance turbine in which the amount of steam leakage in the gaps between the tip portions of the moving blades and stationary blades is reduced. is there.
- a turbine according to the present invention includes a blade disposed in a flow path through which a fluid flows, a structure that is provided at a front end side of the blade via a gap, and that rotates relative to the blade, and the blade and the structure. And a seal fin that projects from one of the two and forms a minute gap with the other.
- the turbine is formed by the blade, the structure, and the seal fin, and includes the fluid inside
- a dead water area filling section is provided so as to fill a dead water area, which is an area where the eddy current does not reach, in a space where the eddy current is generated.
- the dead water area of the space is filled with the dead water area filling portion, it is possible to reduce the loss of energy due to the vortex generated inside the space flowing into the dead water area.
- the eddy current can be strengthened as compared with the case where there is no dead water area filling part, and when the eddy current has a contraction effect, the contraction effect is increased, and the gap between the blade tip and the structure is increased. The amount of fluid leakage can be reduced.
- the dead water filling portion has an inclined surface along the vortex of the fluid.
- the energy loss of the eddy current in the dead water area can be more reliably reduced.
- the vortex can be further strengthened, and when the vortex has a contraction effect, the contraction effect is enhanced, and the amount of fluid leakage can be further reduced.
- the inclined surface is formed into a concave curve in a cross section along the axial direction.
- the inclined surface of the dead water area filling portion can be more accurately aligned with the vortex drawing a curved orbit, the energy loss of the vortex current in the dead water area can be more reliably reduced. be able to.
- the vortex can be further strengthened, and when the vortex has a contraction effect, the contraction effect is enhanced, and the amount of fluid leakage can be further reduced.
- the inclined surface is formed in a substantially linear shape in a cross section along the axial direction.
- the dead water filling portion can be provided in the blade or the structure by a simple process or a simple mold shape.
- the dead water filling portion is provided at a corner portion of the space formed by an axial wall surface along the axial direction and a radial wall surface along the radial direction.
- the corner portion of the blade or the structure is caused by thermal elongation or elongation due to centrifugal force.
- the stress concentration can be reduced. Thereby, damage to the blade and the structure due to stress concentration can be prevented in advance.
- the first seal fin provided on the most upstream side in the axial direction among the seal fins is substantially flush with an axial end surface located at the most upstream part in the axial direction of the blade. Are provided.
- the seal fin protrudes from the blade, and the axial wall surface along the axial direction of the structure has a portion on the upstream side of the first seal fin on the downstream side.
- a step is formed in the radial direction from the portion.
- the seal fin protrudes from the blade side, the minute gap where the fluid leaks is formed at a position close to the structure. Since the axial wall surface of the structure is stepped in the radial direction on the upstream side of the first seal fin, the swirl center of the eddy current comes closer to the minute gap than in the case where there is no stepping. . Therefore, the radial velocity of the vortex in the vicinity of the minute gap is faster in the case of the stepping than in the case of no stepping, and the effect of contraction of the vortex is enhanced, so the amount of fluid leakage in the minute gap Can be further reduced.
- the axial wall surface along the axial direction of the structure includes a portion facing one of the pair of seal fins adjacent to each other along the axial direction and a portion facing the other. A step in the radial direction is provided between them.
- the vortex in the space formed between the pair of adjacent seal fins, the vortex is separated at the corner of the step, and the separation is performed downstream of the vortex at the corner. A vortex is generated. And the amount of fluid leakage in the gap between the downstream seal fin and the structure can be reduced by the contraction effect of the separation vortex.
- the turbine according to the present invention can reduce the amount of fluid leakage in the gap between the blade tip and the structure.
- FIG. 1 is a schematic cross-sectional view showing a steam turbine according to a first embodiment of the present invention.
- FIG. 2 is a partially enlarged cross-sectional view in which the periphery of a tip portion of a moving blade in FIG. 1 is enlarged. It is a figure explaining the contraction flow effect of peeling vortex, Comprising: It is the elements on larger scale which expanded the front-end
- FIG. 1 is a schematic cross-sectional view showing a steam turbine 1 according to the first embodiment.
- the steam turbine 1 is provided with a hollow casing 10, a regulating valve 20 that adjusts the amount and pressure of steam S (fluid) flowing into the casing 10, and a casing 10 that is rotatably provided.
- Casing 10 has an internal space hermetically sealed and a flow path for steam S.
- a ring-shaped partition plate outer ring 11 (structure) into which the shaft body 30 is inserted is firmly fixed to the inner wall surface of the casing 10.
- a plurality of regulating valves 20 are attached to the inside of the casing 10, and each includes a regulating valve chamber 21 into which steam S flows from a boiler (not shown), a valve body 22, and a valve seat 23.
- a regulating valve chamber 21 into which steam S flows from a boiler (not shown), a valve body 22, and a valve seat 23.
- the shaft body 30 includes a shaft main body 31 and a plurality of disks 32 extending radially from the outer periphery of the shaft main body 31.
- the shaft body 30 transmits rotational energy to a machine such as a generator (not shown).
- the annular stationary blade group 40 surrounds the shaft body 30 and is provided at a predetermined interval in the circumferential direction, and a plurality of stationary blades 41 whose base end portions are respectively held by the partition plate outer ring 11, and the stationary blades 41 And a ring-shaped hub shroud 42 that connects the radial front ends to each other in the circumferential direction.
- the shaft 30 is inserted through the hub shroud 42 with a gap having a predetermined width in the radial direction.
- the six annular stator blade groups 40 configured as described above are provided at predetermined intervals in the axial direction of the shaft body 30, and convert the pressure energy of the steam S into velocity energy and are adjacent to the downstream side. It guides to the moving blade 51 side.
- the bearing unit 60 includes a journal bearing device 61 and a thrust bearing device 62, and supports the shaft body 30 in a rotatable manner.
- the annular blade group 50 surrounds the shaft body 30 and is provided at a predetermined interval in the circumferential direction, and a plurality of blades 51 whose base end portions are respectively fixed to the disk 32, and the radial direction of these blades 51 It has a ring-shaped tip shroud (not shown in FIG. 1) that connects the tip portions to each other in the circumferential direction.
- the six annular blade groups 50 configured as described above are provided so as to be adjacent to the downstream side of the six annular stationary blade groups 40. Thereby, the annular stator blade group 40 and the annular rotor blade group 50, which are one set and one stage, are configured in a total of six stages along the axial direction.
- FIG. 2 is a partially enlarged cross-sectional view in which the periphery of the tip of the moving blade 51 in FIG. 1 is enlarged.
- the ring-shaped tip shroud 52 is disposed at the tip of the moving blade 51.
- the chip shroud 52 has a step-like cross-sectional shape, and includes three axial wall surfaces 521a, 521b, and 521c along the axial direction, and three radial wall surfaces 522a, 522b, and 522c along the radial direction. ing.
- the cross-sectional shape of the chip shroud 52 is not limited to the present embodiment, and the design can be changed as appropriate.
- annular groove 111 having a concave cross section is formed on the inner peripheral surface of the outer ring 11 of the partition plate shown in FIG. Then, three seal fins 12 are respectively provided on the bottom surface 111a of the annular groove so as to protrude in the radial direction.
- the first seal fin 12A located on the most upstream side in the steam flow direction, that is, the axial direction, is provided slightly downstream from the radial wall surface 522a of the tip shroud 52, Between the tip and the axial wall surface 521a of the tip shroud 52, a minute gap 13A is formed in the radial direction.
- the second seal fin 12 ⁇ / b> B located on the second upstream side is provided slightly downstream from the radial wall surface 522 b of the tip shroud 52, and its tip and the axial direction of the tip shroud 52 are provided.
- a minute gap 13B is also formed in the radial direction between the wall surface 521b.
- the third seal fin 12 ⁇ / b> C located on the most downstream side is provided slightly downstream from the radial wall surface 522 c of the tip shroud 52, and the tip thereof and the axial wall surface 521 c of the tip shroud 52. Between these, a minute gap 13C is formed in the radial direction.
- the length of the seal fin 12 configured as described above is shortened in the order of the first seal fin 12A, the second seal fin 12B, and the third seal fin 12C.
- the length, shape, installation position, number, and the like of the seal fins 12 are not limited to the present embodiment, and the design can be changed as appropriate according to the cross-sectional shape of the tip shroud 52 and / or the partition plate outer ring 11.
- the dimension of the minute gap 13 is a safe range in which the seal fin 12 and the tip shroud 52 do not contact each other in consideration of the thermal elongation amount of the casing 10 and the moving blade 51, the centrifugal elongation amount of the moving blade, and the like. Of these, it is preferable to set the minimum value.
- the three minute gaps 13 are all set to the same size, but the minute gaps 13 may be set to different dimensions by the seal fins 12 as necessary.
- the seal fin 12 is provided so as to protrude from the outer ring 11 of the partition plate, and the minute gap 13 is formed between the tip shroud 52 and, conversely, the seal fin 12 protrudes from the tip shroud 52.
- the minute gap 13 may be formed between the outer ring 11 and the partition plate outer ring 11.
- the first cavity C1 located on the most upstream side in the axial direction is formed with the bottom surface 111a and the side surface 111b of the annular groove 111 and the first seal fin as shown in FIG. 12A, and the radial wall surface 522a and the axial wall surface 521a of the chip shroud 52 are formed.
- the first cavity C1 formed in this way has a substantially rectangular shape in a cross section along the axial direction.
- the first seal fin 12A is provided slightly downstream from the radial wall surface 522a as described above, the widened portion 14 slightly widened in the axial direction is provided in the axially downstream portion of the first cavity C1. Is formed.
- the two corners of the first cavity C1 more specifically, the corner formed by the bottom surface 111a and the side surface 111b of the annular groove 111, and the bottom surface 111a of the annular groove 111 and the first Dead water area filling portions 15 are respectively provided at corners formed by one seal fin 12A.
- the two dead water zone filling portions 15 are for filling and eliminating the dead water zone generated at the corners of the first cavity C1, and are inclined surfaces formed in a concave curve in a cross section along the axial direction thereof. K.
- the concave curve has a shape that follows the vortex of the steam S generated inside the first cavity C1, and in this embodiment, has an arc shape with a radius of 5 mm or more.
- the size of the dead water filling portion 15 is about 25 times or more in terms of the cross-sectional area compared with the arc-shaped portion having a radius of about 1 mm formed at the corner of the casing to prevent stress concentration as described above. It is the size of.
- the dead water area filling part 15 was comprised as a member different from the partition plate outer ring
- FIG. Further, the position where the dead water area filling portion 15 is provided is not limited to the corner of the first cavity C1, and can be an arbitrary position where the dead water area is generated in the first cavity C1.
- the shape of the inclined surface K is not limited to the arc shape as in the present embodiment, but can be any shape according to the shape of the vortex of the steam S.
- the second cavity C2 located on the second upstream side in the axial direction includes a bottom surface 111a of the annular groove 111, a first seal fin 12A, as shown in FIG.
- the tip shroud 52 is formed by the axial wall surfaces 521a and 521b and the radial wall surface 522b, and the second seal fin 12B.
- the widened portion 16 that is slightly widened in the axial direction is also formed in the axially downstream portion of the second cavity C2 in the same manner as the first cavity C1.
- the dead water filling portions 17 are also provided at the corners formed by the above.
- the roles and shapes of the two dead water zone filling portions 17 are the same as those of the dead water zone filling portion 15 of the first cavity C1.
- the third cavity C3 located on the most downstream side in the axial direction includes a bottom surface 111a of the annular groove 111, a second seal fin 12B, a tip shroud, as shown in FIG. 52, the axial wall surfaces 521b and 521c, the radial wall surface 522c, and the third seal fin 12C.
- the widened portion 18 that is slightly widened in the axial direction is formed in the axially downstream portion of the third cavity C3 as well as the first cavity C1.
- the dead water area filling portions 19 are also provided at the corners formed by the above.
- the roles and shapes of the two dead water zone filling portions 19 are the same as those of the dead water zone filling portion 15 of the first cavity C1.
- the effect of the steam turbine 1 according to the first embodiment will be described with reference to FIGS. 1 and 2.
- the regulating valve 20 shown in FIG. 1 When the regulating valve 20 shown in FIG. 1 is opened, the steam S flows into the casing 10 from a boiler (not shown).
- the steam S is guided to the annular moving blade group 50 by the annular stationary blade group 40 of each stage, and the annular moving blade group 50 starts rotating.
- the energy of the steam S is converted into rotational energy by the annular blade group 50, and this rotational energy is transmitted from the shaft body 30 that rotates integrally with the annular blade group 50 to a generator (not shown) or the like. Is done.
- a part of the main vortex SU1 is peeled off at the corner 52A of the chip shroud 52, so that in the widened portion 14 of the first cavity C1, the main vortex SU1 rotates in the direction opposite to the main vortex SU1, that is, clockwise in FIG. HU1 (vortex) is generated.
- the separation vortex HU1 exhibits a so-called contraction effect that reduces the amount of leakage of the steam S in the minute gap 13A between the first seal fin 12A and the tip shroud 52.
- FIG. 3 is a diagram for explaining the contraction effect of the separation vortex HU1, and is a partially enlarged sectional view in which the periphery of the front end portion of the first seal fin 12A in FIG. 2 is enlarged.
- the clockwise peeling vortex HU1 has a radially inward inertial force immediately before the minute gap 13A between the first seal fin 12A and the tip shroud 52. Therefore, the steam S leaking downstream through the minute gap 13A is pressed down by the inertial force of the separation vortex HU1, so that the width in the radial direction is reduced as shown by the one-dot chain line in FIG.
- the separation vortex HU1 has an effect of reducing the leak amount by compressing the steam S radially inward, that is, a contraction effect.
- the effect of the contraction flow increases as the inertial force of the separation vortex HU1 increases, that is, as the flow velocity of the separation vortex HU1 increases.
- the first cavity C1 is provided with a dead water area filling portion 15 having a substantially arc shape at the two corners along the flow of the main vortex SU1. Therefore, a dead water area, that is, an area that does not reach the main vortex SU1 does not occur at the corner of the first cavity C1. Thereby, it is possible to prevent the energy of the steam S from being lost due to the steam S forming the main vortex SU1 flowing into the dead water area. Then, the main vortex SU1 can be strengthened, and as a result, the separation vortex HU1 that separates from the main vortex SU1 can also be strengthened.
- the contraction effect of the separation vortex HU1 is greater than in the case where there is no dead water filling section 15, and the amount of steam S leaked in the minute gap 13A between the first seal fin 12A and the tip shroud 52 is reduced. be able to.
- the vapor S leaking from the minute gap 13A flows into the second cavity C2.
- the steam S collides with the radial wall surface 522b of the tip shroud 52 to form a counterclockwise main vortex SU2.
- a clockwise peeling vortex HU2 is generated in the widened portion 16 of the second cavity C2.
- the separation vortex HU2 Similar to the separation vortex HU1, the separation vortex HU2 also exhibits a contraction effect that reduces the amount of leakage of the steam S in the minute gap 13B between the second seal fin 12B and the tip shroud 52.
- the second cavity C2 is also provided with a substantially arc-shaped dead water area filling portion 17 at its two corners. Therefore, the main vortex SU2 can be strengthened similarly to the dead water zone filling portion 15 of the first cavity C1, and as a result, the separation vortex HU2 can also be strengthened. Thereby, compared with the case where there is no dead water area filling part 17, the contraction effect of exfoliation eddy HU2 becomes large, and the amount of leakage of steam S in minute gap 13B can be reduced.
- the vapor S leaking from the minute gap 13B flows into the third cavity C3.
- the steam S collides with the radial wall surface 522c of the tip shroud 52 to form a counterclockwise main vortex SU3.
- a clockwise peeling vortex HU3 is generated in the widened portion 18 of the third cavity C3.
- the separation vortex HU3 Similar to the separation vortex HU1, the separation vortex HU3 also exhibits a contraction effect that reduces the leakage amount of the steam S in the minute gap 13C between the third seal fin 12C and the tip shroud 52.
- the third cavity C3 is also provided with a substantially arc-shaped dead water area filling portion 19 at its two corners. Therefore, the main vortex SU3 can be strengthened similarly to the dead water zone filling portion 15 of the first cavity C1, and as a result, the separation vortex HU3 can also be strengthened. Thereby, compared with the case where there is no dead water area filling part 19, the contraction effect of separation vortex HU3 becomes large, and the amount of leakage of steam S in minute gap 13C can be reduced.
- the leakage amount of the steam S can be minimized by reducing the leakage amount of the steam S by the contraction effect of the separation vortices HU1, HU2, and HU3 in the three cavities C1, C2, and C3. It has become.
- the number of cavities C along the axial direction is not limited to three, and an arbitrary number can be provided.
- the dead water area filling section 15 is provided in the first cavity C
- the dead water area filling section 17 is provided in the second cavity C2
- the dead water area filling section 19 is provided in the third cavity C3. It is not necessary to provide a dead water area filling part in C, and it is sufficient if at least one cavity C is provided with a dead water area filling part.
- the steam turbine according to this embodiment differs from the steam turbine 1 according to the first embodiment in the position where the dead water region filling portion is provided in the cavity C formed around the tip of the moving blade 51. Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 4 is a schematic cross-sectional view showing the periphery of the tip of the rotor blade 51 of the second embodiment. Similar to the first embodiment, three cavities C are formed between the annular blade group 50 and the partition plate outer ring 11. Of the three cavities C, the first cavity C1 located on the most upstream side in the axial direction is not provided with a dead water filling portion.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in FIG.
- the second cavity C2 located on the second upstream side in the axial direction is provided with a dead water filling portion 70 at one corner thereof. It has been.
- the dead water filling portion 70 has a substantially arc-shaped inclined surface K in a cross section along the axial direction, and is provided at a corner formed by the axial wall surface 521a and the radial wall surface 522b of the chip shroud 52. Yes.
- the third cavity C3 located on the most downstream side in the axial direction is provided with a dead water filling portion 71 at one corner thereof. Yes.
- the dead water region filling portion 71 also has a substantially arc-shaped inclined surface K, and is provided at a corner formed by the axial wall surface 521b and the radial wall surface 522c of the tip shroud 52.
- a dead water area filling portion 70 having a substantially arc-shaped inclined surface K is provided at one corner of the second cavity C2. Accordingly, the main vortex SU2 can be strengthened by preventing the loss of the energy of the steam S in the dead water area, and as a result, the separation vortex HU2 can also be strengthened. Thereby, compared with the case where there is no dead water area filling part 70, the contraction effect of the separation vortex HU2 is increased, and the leakage amount of the steam S in the minute gap 13B can be reduced.
- the dead water filling portion 70 is provided at a corner formed by the axial wall surface 521a and the radial wall surface 522b of the chip shroud 52. Therefore, it is possible to alleviate the occurrence of stress concentration due to thermal elongation or elongation due to centrifugal force at the corners 52B and 52C of the tip shroud 52 formed by the axial wall surface 521a and the radial wall surface 522b and having a sharp shape. it can.
- a dead water area filling portion 71 having a substantially arc-shaped inclined surface K is also provided at one corner of the third cavity C3. Therefore, since the separation vortex HU3 can be strengthened by strengthening the main vortex SU3, the leakage amount of the steam S in the minute gap 13C can be reduced as compared with the case where there is no dead water area filling portion 71.
- the dead water region filling portion 71 is provided at a corner formed by the axial wall surface 521b and the radial wall surface 522c of the tip shroud 52. Therefore, stress concentration caused by thermal elongation or elongation due to centrifugal force can be mitigated in the corners 52B and 52C of the tip shroud 52 having a sharp shape.
- the steam turbine according to this embodiment is also different from the steam turbine 1 of the first embodiment in the position where the dead water region filling portion is provided in the cavity C formed around the tip of the moving blade 51. Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 5 is a schematic cross-sectional view showing the periphery of the tip portion of the rotor blade 51 of the third embodiment. Similar to the first embodiment, three cavities C are formed between the annular blade group 50 and the partition plate outer ring 11. Of the three cavities C, the first cavity C1 located on the most upstream side in the axial direction is provided with the dead water filling portion 15 at the same two corners as in the first embodiment shown in FIG. It has been.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in FIG.
- the second cavity C ⁇ b> 2 located on the second upstream side in the axial direction has the same two corners as in the first embodiment shown in FIG. 2.
- a dead water area filling portion 17 is provided respectively, and a dead water area filling portion 70 is also provided at the same corner as in the second embodiment shown in FIG.
- the third cavity C3 located on the most downstream side in the axial direction also has a dead water area at the same two corners as in the first embodiment shown in FIG.
- Each of the filling portions 19 is provided, and a dead water area filling portion 71 is also provided at the same corner as in the second embodiment shown in FIG.
- the second cavity C ⁇ b> 2 is further provided with a dead water zone filling unit 70 in addition to the two dead water zone filling units 17, so that the energy of the steam S is compared with the first embodiment. Can be further prevented from being lost in the dead water area.
- the main vortex SU2 can be further strengthened, the separation vortex HU2 can be further strengthened, and the leak amount of the steam S in the minute gap 13B can be further reduced as compared with the first embodiment.
- the leak amount of the steam S in the minute gap 13C can be further reduced from the first embodiment for the same reason as the second cavity C2.
- the heat shrunk or the centrifugal force causes the extension. It is possible to alleviate the occurrence of stress concentration at the location.
- the steam turbine according to the fourth embodiment of the present invention differs in the position and shape of the dead water region filling portion in the cavity C formed around the tip of the moving blade 51. . Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 6 is a schematic cross-sectional view showing the periphery of the tip of the moving blade 51 of the fourth embodiment. Similar to the first embodiment, three cavities C are formed between the annular blade group 50 and the partition plate outer ring 11. The three cavities C are each provided with a dead water area filling portion at the same corner as in the third embodiment shown in FIG. 5, but the shape of the inclined surface K of each dead water area filling portion is the third embodiment. It is different from the form.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in FIG.
- the first cavity C1 located on the most upstream side in the axial direction includes the same two as in the first embodiment shown in FIG.
- a dead water filling portion 72 having an inclined surface K having a substantially elliptic arc shape is provided at the corner.
- the second cavity C2 located on the second upstream side in the axial direction is also provided with a dead water filling portion 73 having an inclined surface K having a substantially elliptic arc shape at the same two corners as in the first embodiment.
- a dead water filling portion 74 having an inclined surface K having a substantially elliptic arc shape is provided at the same corner as in the second embodiment.
- the third cavity C3 located on the most downstream side in the axial direction is provided with a dead water area filling portion 75 having an inclined surface K having a substantially elliptic arc shape at the same two corners as in the first embodiment.
- a dead water filling portion 76 having an inclined surface K having a substantially elliptic arc shape is provided.
- the effects of the steam turbine 1 according to the fourth embodiment will be described focusing on differences from the third embodiment.
- the steam turbine 1 according to the third embodiment exhibits.
- the main vortices SU1, SU2, SU3 generated in the three cavities C generally have a cross-sectional shape along the axial direction that is elliptical rather than a perfect circle.
- the shape of the inclined surface K of the dead water area filling portions 72 to 76 is also substantially elliptical arc shape so as to more accurately follow the shape of the water, the energy of the steam S flows into the dead water area and the energy is lost. It is because it can prevent more reliably than embodiment.
- the inclined surface K of the dead water filling portion 72, 73, 75 provided on the partition plate outer ring 11 side has a substantially elliptical arc shape that is vertically long in the radial direction.
- the inclined surfaces K of the dead water filling portions 74 and 76 provided on the tip shroud 52 side have a substantially elliptical arc shape that is vertically long in the axial direction.
- the separation vortices HU1, HU2, and HU3 have an inertial force in the radial direction immediately before the minute gaps 13A, 13B, and 13C, so that the contraction effect of the separation vortices HU1, HU2, and HU3 is increased. Can do. It should be noted that it is possible to change the design appropriately as to whether the inclined surface K of the dead water filling section 72 to 76 is formed in a substantially elliptical elliptical shape in either the axial direction or the radial direction.
- the steam turbine according to the fifth embodiment of the present invention differs in the position and shape of the dead water region filling portion in the cavity C formed around the tip of the moving blade 51. . Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 7 is a schematic cross-sectional view showing the periphery of the tip of the moving blade 51 of the fifth embodiment. Similar to the first embodiment, three cavities C are formed between the annular blade group 50 and the partition plate outer ring 11. The three cavities C are each provided with a dead water area filling portion at the same corner as in the third embodiment shown in FIG. 5, but the shape of the inclined surface K of each dead water area filling portion is the third embodiment. It is different from the form.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in FIG.
- the first cavity C1 located on the most upstream side in the axial direction includes the same two as in the first embodiment shown in FIG.
- a dead water area filling portion 77 having a substantially linear inclined surface K is provided at the corner.
- the second cavity C2 located upstream of the second surface along the axial direction there is a dead water area filling portion 78 having a substantially linear inclined surface K at the same two corners as in the first embodiment.
- a dead water filling portion 79 having a substantially linear inclined surface K is provided at the same corner as in the second embodiment.
- the third cavity C3 located on the most downstream side in the axial direction is also provided with a dead water area filling portion 80 having a substantially linear inclined surface K at the same two corners as in the first embodiment.
- a dead water area filling portion 81 having a substantially linear inclined surface K is provided.
- the operational effects of the steam turbine 1 according to the fifth embodiment will be described focusing on differences from the third embodiment.
- the steam turbine 1 according to the third embodiment exhibits.
- the dead water filling parts 77 to 81 are integrally formed with the partition plate outer ring 11 and the chip shroud 52, the shape of the mold for forming the partition plate outer ring 11 and the chip shroud 52 is simplified. be able to.
- the dead water area filling portions 77 to 81 have only one substantially linear inclined surface K has been described as an example.
- the dead water area filling portions 77 to 81 have an approximately linear inclined surface K. You may have two or more. That is, the cross-sectional shape of the dead water filling parts 77 to 81 is not limited to a triangle as in this embodiment, but may be a polygon.
- the configuration of the steam turbine according to the sixth embodiment of the present invention will be described.
- the position where the dead water area filling portion is provided is not the periphery of the tip portion of the moving blade 51 but the periphery of the tip portion of the stationary blade 41. Is different. Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- the annular stationary blade group 40 corresponds to a blade according to the present invention
- the shaft body 30 corresponds to a structure according to the present invention.
- FIG. 8 is a partially enlarged cross-sectional view in which the vicinity of the tip of the stationary blade 41 of the sixth embodiment is enlarged.
- the ring-shaped hub shroud 42 is disposed at the tip of the stationary blade 41.
- Three seal fins 84 are provided on the outer peripheral surface 42a of the hub shroud 42 so as to protrude in the radial direction.
- the first seal fin 84A provided on the most upstream side in the axial direction is substantially flush with the axial end surface 42b located at the most upstream portion in the axial direction of the hub shroud 42. It is provided to form.
- annular groove 301 having a concave cross section is formed on the outer peripheral surface of the shaft body 30, and a portion having a small diameter due to the formation of the annular groove 301 is inserted into the hub shroud 42. Thereby, a minute gap 85 is formed in the radial direction between the bottom surface 301 a of the annular groove 301 and each seal fin 84.
- the length, shape, installation position, number, and the like of the seal fins 84 are not limited to this embodiment, and the design can be changed as appropriate according to the cross-sectional shape of the hub shroud 42 and / or the shaft body 30.
- the dimension of the minute gap 85 is preferably set to a minimum value within a safe range where the seal fin 84 and the shaft body 30 do not contact each other.
- the seal fin 84 is provided so as to protrude from the hub shroud 42 and the minute gap 85 is formed between the seal body 84 and the shaft body 30, but conversely, the seal fin 84 protrudes from the shaft body 30. It may be provided and a minute gap 85 may be formed between the hub shroud 42 and the hub shroud 42.
- the fourth cavity C4 located on the most upstream side in the axial direction is provided with the bottom surface 301a and the side surface 301b of the annular groove 301 and the first seal fin as shown in FIG. 84A and the axial end surface 42b of the hub shroud 42 are formed.
- the fourth cavity C4 thus formed has a substantially rectangular shape with a cross section along the axial direction.
- a dead water filling portion 86 is provided at one corner of the fourth cavity C4, more specifically at the corner formed by the bottom surface 301a and the side surface 301b of the annular groove 301. It has been.
- This one dead water region filling part 86 has a substantially elliptic arc-shaped inclined surface K in a cross section along the axial direction thereof.
- the role of the dead water area filling part 86 is the same as that of 1st Embodiment.
- the shape of the inclined surface K of the dead water region filling portion 86 is not limited to a substantially elliptic arc shape as in the present embodiment, but may be a substantially arc shape or a substantially linear shape.
- the dead water filling portion 86 is provided only in the fourth cavity among the three cavities C. However, the fifth cavity C5 located on the second upstream side or the sixth cavity located on the most downstream side. You may provide a dead water zone filling part also in the cavity C6.
- the dead water region filling portion is also formed in the corner portion formed by the outer peripheral surface 42a of the hub shroud 42 and the second seal fin 84B, or in the corner portion formed by the outer peripheral surface 42a of the hub shroud 42 and the third seal fin 84C. May be provided.
- the steam S that has flowed into the casing 10 shown in FIG. 1 originally passes between the plurality of stationary blades 41 constituting the annular stationary blade group 40 and is guided to the annular moving blade group 50.
- a part of S leaks downstream through a minute gap 85 (85A, 85B, 85C) between the annular stationary blade group 40 and the shaft body 30.
- the main vortex SU4 since the main vortex SU4 rotates clockwise, the main vortex SU4 has a radially outward inertial force immediately before the minute gap 85A. Accordingly, the main vortex SU4 exerts a contraction effect that reduces the leak amount by compressing the steam S leaking downstream through the minute gap 85A.
- the fourth cavity C4 is provided with a dead water area filling portion 86 having a substantially elliptic arc shape at one corner thereof along the flow of the main vortex SU4. Therefore, the dead water area generated in the fourth cavity C4 can be reduced, and loss of energy due to the flow of the steam S into the dead water area can be reduced. As a result, the main vortex SU4 can be strengthened as compared with the case where there is no dead water filling section 86, and as a result, the contraction effect of the main vortex SU4 is increased, and the amount of leakage of the steam S in the minute gap 85A is reduced. be able to.
- the steam turbine according to the present embodiment differs from the steam turbine according to the sixth embodiment in the shape of the cavity located on the most upstream side in the axial direction. Since the other configuration is the same as that of the sixth embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 9 is a partial enlarged cross-sectional view in which the periphery of the tip portion of the stationary blade 41 of the seventh embodiment is enlarged.
- three cavities C are formed between the annular stator blade group 40 and the shaft body 30.
- the seal fin 84 can be provided so as to protrude from the shaft body 30 instead of the hub shroud 42 side.
- the seal fin 84 is provided on the hub shroud 42 side. Is an essential configuration and cannot be provided in the shaft body 30. It is not limited to the vicinity of the tip of the stationary blade 41, and a seal fin 84 is provided so as to protrude from the tip shroud 52 constituting the rotor blade 51, and a portion upstream of the seal fin 84 is arranged in a radial direction from a downstream portion. You may form so that it may step down, ie, may be located in the radial direction outer side.
- the dead water area filling parts 87 and 88 are provided in the two corners of the seventh cavity C7, respectively. More specifically, a dead water region filling portion 87 is provided at a corner portion formed by the bottom surface 301a and the side surface 301b of the annular groove 301, and a corner portion formed by the bottom surface 301a and the step surface 301c is filled with a dead water region. A portion 88 is provided. These two dead water zone filling portions 87 and 88 each have a substantially elliptic arc-shaped inclined surface K in a cross section along the axial direction thereof.
- the effects of the steam turbine 1 according to the seventh embodiment will be described focusing on differences from the sixth embodiment.
- the first seal fins 84 ⁇ / b> A are provided so as to protrude from the hub shroud 42, whereby the position where the minute gap 85 ⁇ / b> A is formed is a position close to the shaft body 30.
- the seventh cavity C7 on the upstream side from the minute gap 85A is formed to be stepped down from the eighth cavity C8 and the ninth cavity C9 on the downstream side.
- the main vortex SU5 that rotates clockwise inside the seventh cavity C7 passes through the minute gap 85A and reaches further downward (inward in the radial direction). Accordingly, in the main vortex SU5 of this embodiment, the center of rotation of the main vortex SU5 approaches the minute gap 85A as compared to the case where there is no stepping down as in the sixth embodiment shown in FIG. Accordingly, the radial velocity of the main vortex SU5 in the vicinity of the minute gap 85A is faster when there is a step than when there is no step, and the contraction effect of the main vortex SU5 is increased. The leak amount of the steam S can be further reduced.
- the dead water filling portions 87 and 88 are provided at the two corners of the seventh cavity C7, only at one corner of the fourth cavity C4 as in the sixth embodiment. Compared with the case where the dead water area filling part 86 is provided, the dead water area can be further reduced and the main vortex SU5 can be further strengthened. Thereby, this embodiment produces the effect that the leak amount of the vapor
- the steam turbine according to the present embodiment is different in shape of each cavity from the steam turbine according to the sixth embodiment. Since the other configuration is the same as that of the sixth embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 10 is a partially enlarged cross-sectional view in which the vicinity of the tip of the stationary blade 41 of the eighth embodiment is enlarged. Similar to the seventh embodiment, three cavities C are formed between the annular stator blade group 40 and the shaft body 30. However, among the three cavities C, the tenth cavity C10 located on the most upstream side has the same configuration as the seventh cavity C7 of the seventh embodiment, but the eleventh cavity C11 and the twelfth cavity located on the downstream side thereof. The configuration of C12 is different from the eighth cavity C8 and the ninth cavity C9 of the seventh embodiment.
- the bottom surface 301a of the annular groove 301 has a downstream side along the axial direction at a position between the first seal fin 84A and the second seal fin 84B adjacent to each other.
- a stepped portion 89 is formed so as to step inward in the radial direction from the upstream side.
- a widened portion 90 that is slightly widened in the radial direction is formed in the axially downstream portion of the eleventh cavity C11.
- the radial height position of the bottom surface 301a is a height position substantially equal to the bottom surface 301a forming the tenth cavity C10.
- the bottom surface 301a on the downstream side of the stepped portion 89 may be at a different height from the bottom surface 301a that forms the tenth cavity C10.
- the dead water area filling parts 87 and 88 are each provided in the two corners of 10th cavity C10 similarly to 7th Embodiment.
- a dead water area filling portion 82 and a dead water area filling portion 83 are provided at three corners of the eleventh cavity C11. More specifically, the corner formed by the outer peripheral surface 42a of the hub shroud 42 and the first seal fin 84A and the corner formed by the outer peripheral surface 42a and the second seal fin 84B are filled with dead water.
- Each part 82 is provided.
- a dead water filling portion 83 is provided at a corner formed by the step portion 89 and the bottom surface 301a.
- the clockwise main vortex SU5 is formed inside the tenth cavity C10, similarly to the seventh cavity C7 of the seventh embodiment, and has the same effect as the seventh embodiment. Play.
- the vapor S flowing from the tenth cavity C10 to the eleventh cavity C11 through the minute gap 85A forms a counterclockwise main vortex SU6 inside the eleventh cavity C11. .
- a part of the main vortex SU6 is peeled off at the corner portion of the step portion 89, whereby a clockwise peeling vortex HU4 is generated.
- this separation vortex HU4 has a radially inward inertial force immediately before the minute gap 85B between the second seal fin 84B and the shaft body 30, it exerts a large contraction effect. .
- the step portion 89 is not formed in the eleventh cavity C11, and this embodiment is formed at the tip portion of the second seal fin 84B as compared with the case where only the counterclockwise main vortex SU6 is generated therein. There is an effect that the leakage amount of the steam S in the minute gap 85B can be further reduced.
- the eleventh cavity C11 is provided with a dead water area filling portion 82 along the flow of the main vortex SU6 at its two corners, and at one corner with a separation vortex.
- a dead water area filling portion 83 is provided along the flow of the HU 4. Therefore, it is possible to reduce the loss of energy by flowing into the dead water area for both the main vortex SU6 and the separation vortex HU4. As a result, both the main vortex SU6 and the separation vortex HU4 can be strengthened as compared with the case without the dead water area filling portions 82 and 83, so that the leakage amount of the steam S in the minute gap 85B can be reduced.
- the stepped portion 89 is formed so that the downstream side is stepped radially inward from the upstream side along the axial direction.
- the step portion 91 may be formed so as to rise one step radially outward from the upstream side.
- a widened portion 92 that is slightly widened in the axial direction is formed in the axially downstream portion of the eleventh cavity C11.
- the corner formed by the outer peripheral surface 42a of the hub shroud 42 and the first seal fin 84A and the corner formed by the outer peripheral surface 42a and the second seal fin 84B are A dead water area filling section 82 is provided.
- a dead water filling portion 100 is provided at a corner formed by the step portion 91 and the bottom surface 301a.
- the vapor S flowing from the tenth cavity C10 to the eleventh cavity C11 through the minute gap 85A also forms the main vortex SU7 within the eleventh cavity C11.
- a part of the main vortex SU7 is peeled off at the corner portion of the step portion 91, whereby a clockwise peeling vortex HU5 is generated.
- the eleventh cavity C11 is provided with dead water filling portions 82 at two corners, so that the energy loss of the main vortex SU7 can be reduced as in the configuration of FIG.
- the dead water filling portion 100 is provided at one corner, the energy loss of the separation vortex HU5 can also be reduced.
- FIG. 12 is a schematic cross-sectional view showing the periphery of the tip end portion of the moving blade 51 of the ninth embodiment, and particularly an enlarged view of the tip end portion of the first seal fin 93.
- symbol is used and description is abbreviate
- the first seal fin 93 includes a fin main body 931 and a space restricting portion 932 formed wider than the fin main body 931.
- the first cavity C1 upstream from the first seal fin 93 has a widened portion 94 that is slightly widened in the axial direction at the downstream side in the axial direction.
- a dead water area filling portion 95 is provided at a corner portion of the widened portion 94, more specifically at a corner portion formed by the fin main body portion 931 and the space limiting portion 932.
- the counterclockwise main vortex SU ⁇ b> 1 formed in the first cavity C ⁇ b> 1 is partially peeled off at the corner portion of the tip shroud 52, so that the inside of the widened portion 94 is A clockwise peeling vortex HU1 is generated.
- the separation vortex HU1 collides with the space restricting portion 932 and the fin main body portion 931, and the flow direction thereof is guided, whereby the flow of the vortex flow is strengthened.
- the dead water region filling portion 95 is provided at the corner of the widened portion 94, it is possible to reduce the loss of energy of the steam S due to the separation vortex HU1 flowing into the dead water region. Thereby, compared with the case where there is no dead water area filling portion 95, the separation vortex HU1 can be strengthened to increase the contraction effect thereof, so that the amount of leakage of the steam S in the minute gap 13A can be reduced.
- the steam turbine according to this embodiment differs from the steam turbine 1 according to the first embodiment in the position where the dead water region filling portion is provided in the cavity C formed around the tip of the moving blade 51. Since the other configuration is the same as that of the first embodiment, the same reference numerals are used and description thereof is omitted here.
- FIG. 13 is a schematic cross-sectional view showing the periphery of the tip of the moving blade 51 of the tenth embodiment. Similar to the first embodiment, three cavities C are formed between the annular blade group 50 and the partition plate outer ring 11. Here, in this embodiment, the separation distance in the axial direction from the seal fins 12A, 12B, and 12C to the radial wall surfaces 522a, 522b, and 522c is set longer than that in the first embodiment. Accordingly, the widened portions 96, 97, and 98 of the three cavities C1, C2, and C3 are formed wider than in the first embodiment.
- the first cavity C1 located on the most upstream side in the axial direction is provided with the dead water filling portion 15 at the two corners as in the first embodiment. Yes. More specifically, the dead water filling portion 15 is formed at the corner formed by the bottom surface 111a and the side surface 111b of the annular groove 111 and at the corner formed by the bottom surface 111a of the annular groove 111 and the first seal fin 12A. Is provided.
- the first cavity C1 is provided with a dead water area filling portion 99 at an intermediate position between the two corners of the bottom surface 111a of the annular groove 111.
- the dead water filling portion 99 has two inclined surfaces K1 and K2, and one inclined surface K1 has the other inclined surface K2 so as to follow the flow of the main vortex SU1 generated in the first cavity C1. Are formed so as to follow the flow of the separation vortex HU1 generated in the widened portion 96 of the first cavity C1.
- the second cavity C2 and the third cavity C3 are also provided with dead water filling portions 17 and 19 at the two corners, respectively, and between the two corners of the bottom surface 111a.
- a dead water area filling section 99 is provided at each position.
- the separation vortex HU1 can be strengthened indirectly by strengthening the main vortex SU1, and the separation vortex HU1 can also be strengthened directly.
- the contraction effect of the separation vortex HU1 is increased as compared with the case where there is no dead water area filling portion 15, 15, 99, so that the amount of leakage of the steam S in the minute gap 13A can be reduced.
- the present invention provides a blade disposed in a flow path through which a fluid flows, a structure that is provided on the tip side of the blade via a gap, and that rotates relative to the blade, and either the blade or the structure.
- a turbine provided with a seal fin that protrudes from one side and forms a minute gap with the other, and is formed by the blade, the structure, and the seal fin, and the vortex of the fluid is formed inside the turbine.
- the present invention relates to a turbine in which a dead water area filling section is provided so as to fill a dead water area, which is an area where the eddy current does not reach, in a generated space.
- the eddy current can be strengthened as compared with the case where there is no dead water area filling portion, and when the eddy current has a contraction effect, the contraction effect is increased, and the blade tip and the structure are separated. The amount of fluid leakage in the gap can be reduced.
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Abstract
Description
本願は、2010年9月28日に日本に出願された特願2010-217218号に優先権を主張し、その内容をここに援用する。
衝動タービンとは、静翼がノズル形状を有し、この静翼を通過した蒸気が動翼に噴射され、蒸気から受ける衝撃力だけによって動翼が回転するものである。一方、反動タービンは、静翼の形状は動翼と同様であって、この静翼を通過した蒸気から受ける衝撃力と、動翼を通過する際に生じる蒸気の膨張に対する反動力とによって動翼が回転するものである。
以下、図面を参照して本発明の実施の形態について説明する。まず、本発明の第1実施形態に係る蒸気タービンの構成について説明する。図1は、第1実施形態に係る蒸気タービン1を示す概略断面図である。
蒸気タービン1は、中空のケーシング10と、このケーシング10の内部に流入する蒸気S(流体)の量と圧力を調整する調整弁20と、ケーシング10の内部に回転自在に設けられ、不図示の発電機等の機械に動力を伝達する軸体30と、ケーシング10に保持された環状静翼群40と、軸体30に設けられた環状動翼群50(ブレード)と、軸体30を軸回りに回転可能に支持する軸受部60と、を備えている。
そして、このように構成される6個の環状静翼群40が、軸体30の軸方向に所定間隔で設けられており、蒸気Sの圧力エネルギーを速度エネルギーに変換して、下流側に隣接する動翼51側に案内するようになっている。
そして、このように構成される6個の環状動翼群50が、6個の環状静翼群40の下流側に隣接するようにしてそれぞれ設けられている。これにより、1組1段とされる環状静翼群40及び環状動翼群50が、軸方向に沿って合計6段に構成されている。
また、本実施形態では、シールフィン12を仕切板外輪11から突出して設け、チップシュラウド52との間に微小隙間13を形成したが、これとは逆に、シールフィン12をチップシュラウド52から突出して設け、仕切板外輪11との間に微小隙間13を形成してもよい。
次に、本発明の第2実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置が異なっている。それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
次に、本発明の第3実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンも、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置が異なっている。それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
次に、本発明の第4実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置及びその形状が異なっている。それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
また、軸方向に沿って2番目に上流側に位置する第2キャビティC2にも、第1実施形態と同じ2つの隅部に、略楕円弧形状の傾斜面Kを有する死水域充填部73が設けられるとともに、第2実施形態と同じ1つの隅部に、略楕円弧形状の傾斜面Kを有する死水域充填部74が設けられている。
更に、軸方向に沿って最も下流側に位置する第3キャビティC3にも、第1実施形態と同じ2つの隅部に、略楕円弧形状の傾斜面Kを有する死水域充填部75が設けられるとともに、第2実施形態と同じ1つの隅部に、略楕円弧形状の傾斜面Kを有する死水域充填部76が設けられている。
これは、3つのキャビティCに発生する主渦SU1,SU2,SU3の軸方向に沿った断面形状は、真円よりも楕円になる方が一般的であるため、この主渦SU1,SU2,SU3の形状により正確に沿うように、死水域充填部72~76の傾斜面Kの形状も略楕円弧形状とした方が、蒸気Sが死水域に流入してそのエネルギーが損失することを、第3実施形態より一層確実に防止できるからである。
次に、本発明の第5実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置及びその形状が異なっている。それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
また、軸方向に沿って2番面に上流側に位置する第2キャビティC2にも、第1実施形態と同じ2つの隅部に、略直線状の傾斜面Kを有する死水域充填部78が設けられるとともに、第2実施形態と同じ1つの隅部に、略直線状の傾斜面Kを有する死水域充填部79が設けられている。
更に、軸方向に沿って最も下流側に位置する第3キャビティC3にも、第1実施形態と同じ2つの隅部に、略直線状の傾斜面Kを有する死水域充填部80が設けられるとともに、第2実施形態と同じ1つの隅部に、略直線状の傾斜面Kを有する死水域充填部81が設けられている。
次に、本発明の第6実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、死水域充填部を設ける位置が、動翼51の先端部周辺ではなく、静翼41の先端部周辺である点で異なっている。それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。尚、本実施形態では、環状静翼群40が本願発明に係るブレードに相当し、軸体30が本願発明に係る構造体に相当する。
次に、本発明の第7実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第6実施形態の蒸気タービンと比較すると、軸方向に沿って最も上流側に位置するキャビティの形状が異なっている。それ以外の構成については第6実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
従って、本実施形態の主渦SU5は、図8に示す第6実施形態のように段落ちの無い場合と比較すると、主渦SU5の旋回中心が微小隙間85Aに近付くことになる。従って、微小隙間85Aの付近における主渦SU5の径方向速度は、段落ちのある場合の方が段落ちの無い場合より速くなり、主渦SU5の縮流効果が高くなるため、微小隙間85Aにおける蒸気Sのリーク量を一層低減化することができる。
また、本実施形態では、第7キャビティC7の2つの隅部に、死水域充填部87,88が設けられているので、第6実施形態のように第4キャビティC4の1つの隅部だけに死水域充填部86が設けられている場合と比較すると、死水域を更に減らして主渦SU5を一層強めることができる。
これにより、本実施形態は、第6実施形態と比較して、微小隙間85Aにおける蒸気Sのリーク量を一層低減させることができるという効果を奏する。
次に、本発明の第8実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第6実施形態の蒸気タービンと比較すると、各キャビティの形状が異なっている。それ以外の構成については第6実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
これにより、第11キャビティC11の軸方向下流部には、径方向に若干拡幅された拡幅部90が形成されている。そして、段差部89より下流側では、底面301aの径方向高さ位置は、第10キャビティC10を形成する底面301aと略等しい高さ位置になっている。尚、段差部89より下流側における底面301aは、第10キャビティC10を形成する底面301aと異なる高さ位置であってもよい。
そして、図10に示す構成と同様に、ハブシュラウド42の外周面42aと第1シールフィン84Aとによって形成される隅部、及び外周面42aと第2シールフィン84Bによって形成される隅部には、死水域充填部82がそれぞれ設けられている。更に、段差部91と底面301aとによって形成される隅部には、死水域充填部100が設けられている。
次に、本発明の第9実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置が異なっている。ここで、図12は、第9実施形態の動翼51の先端部周辺を示す概略断面図であって、特に、第1シールフィン93の先端部について拡大した図である。尚、第1シールフィン93以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
次に、本発明の第10実施形態に係る蒸気タービンの構成について説明する。本実施形態に係る蒸気タービンは、第1実施形態の蒸気タービン1と比較すると、動翼51の先端部周辺に形成されるキャビティCにおいて、死水域充填部を設ける位置が異なっている。
それ以外の構成については第1実施形態と同じであるため、同じ符号を用い、ここでは説明を省略する。
同様に、本実施形態における第2キャビティC2及び第3キャビティC3においても、合計3個の死水域充填部17,17,99及び19,19,99がそれぞれ設けられており、第1キャビティC1と同様の作用効果が得られるため、微小隙間13B,13Cにおける蒸気Sのリーク量を低減させることができる。
10 ケーシング
11 仕切板外輪(構造体)
111 環状溝
111a 底面
111b 側面
12 シールフィン
12A 第1シールフィン
12B 第2シールフィン
12C 第3シールフィン
13 微小隙間
13A 微小隙間
13B 微小隙間
13C 微小隙間
14 拡幅部
15 死水域充填部
16 拡幅部
17 死水域充填部
18 拡幅部
19 死水域充填部
20 調整弁
21 調整弁室
22 弁体
23 弁座
24 蒸気室
30 軸体(構造体)
301 環状溝
301a 底面
301b 側面
301c 段差面
31 軸本体
32 ディスク
40 環状静翼群(ブレード)
41 静翼
42 ハブシュラウド
42A 角部
42a 外周面
42b 軸方向端面
50 環状動翼群(ブレード)
51 動翼
52 チップシュラウド
52A 角部
52B 角部
52C 角部
521a 軸方向壁面
521b 軸方向壁面
521c 軸方向壁面
522a 径方向壁面
522b 径方向壁面
522c 径方向壁面
60 軸受部
61 ジャーナル軸受装置
62 スラスト軸受装置
70 死水域充填部
71 死水域充填部
72 死水域充填部
73 死水域充填部
74 死水域充填部
75 死水域充填部
76 死水域充填部
77 死水域充填部
78 死水域充填部
79 死水域充填部
80 死水域充填部
81 死水域充填部
82 死水域充填部
83 死水域充填部
84 シールフィン
84A 第1シールフィン
84B 第2シールフィン
84C 第3シールフィン
85 微小隙間
85A 微小隙間
85B 微小隙間
85C 微小隙間
86 死水域充填部
87 死水域充填部
88 死水域充填部
89 段差部
90 拡幅部
91 段差部
92 拡幅部
93 第1シールフィン
931 フィン本体部
932 空間制限部
94 拡幅部
95 死水域充填部
96 拡幅部
97 拡幅部
98 拡幅部
99 死水域充填部
C キャビティ
C1 第1キャビティ
C10 第10キャビティ
C11 第11キャビティ
C12 第12キャビティ
C2 第2キャビティ
C3 第3キャビティ
C4 第4キャビティ
C5 第5キャビティ
C6 第6キャビティ
C7 第7キャビティ
C8 第8キャビティ
C9 第9キャビティ
HU1 剥離渦
HU2 剥離渦
HU3 剥離渦
HU4 剥離渦
HU5 剥離渦
K 傾斜面
K1 傾斜面
K2 傾斜面
S 蒸気
SU1 主渦
SU2 主渦
SU3 主渦
SU4 主渦
SU5 主渦
SU6 主渦
SU7 主渦
Claims (8)
- 流体が流れる流路に配置されるブレードと、該ブレードの先端側に隙間を介して設けられ、前記ブレードに対して相対回転する構造体と、前記ブレード及び前記構造体のいずれか一方から突出して設けられ、他方との間に微小隙間を形成するシールフィンと、を備えるタービンであって、
前記ブレード、前記構造体、及び前記シールフィンによって形成され、内部で前記流体の渦流が発生する空間に、前記渦流が及ばない領域である死水域を埋めるようにして、死水域充填部が設けられているタービン。 - 前記死水域充填部が、前記流体の渦流に沿う傾斜面を有している請求項1に記載のタービン。
- 前記傾斜面が、軸方向に沿った断面で凹状の曲線に形成されている請求項2に記載のタービン。
- 前記傾斜面が、軸方向に沿った断面で略直線状に形成されている請求項2に記載のタービン。
- 前記死水域充填部が、軸方向に沿う軸方向壁面と径方向に沿う径方向壁面とによって形成される前記空間の隅部に設けられている請求項1から4のいずれか1項に記載のタービン。
- 前記シールフィンのうち軸方向に沿って最も上流側に設けられた第1シールフィンが、前記ブレードの軸方向最上流部に位置する軸方向端面と略同一面を形成するように設けられている請求項1から5のいずれか1項に記載のタービン。
- 前記シールフィンが、前記ブレードから突出して設けられ、前記構造体の軸方向に沿う軸方向壁面は、前記第1シールフィンより上流側の部分が、下流側の部分より径方向に段落ちして形成されている請求項6に記載のタービン。
- 前記構造体の軸方向に沿う軸方向壁面は、軸方向に沿って互いに隣接する一対の前記シールフィンの一方に対向する部分と、他方に対向する部分との間に、径方向への段差が設けられている請求項6又は7に記載のタービン。
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CN201180029455.0A CN102959184B (zh) | 2010-09-28 | 2011-09-15 | 透平机 |
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US20130129493A1 (en) | 2013-05-23 |
EP2623722B1 (en) | 2019-12-18 |
JP2012072689A (ja) | 2012-04-12 |
EP2623722A4 (en) | 2017-12-13 |
JP5709447B2 (ja) | 2015-04-30 |
US9429022B2 (en) | 2016-08-30 |
KR20130041828A (ko) | 2013-04-25 |
KR101464850B1 (ko) | 2014-11-25 |
EP2623722A1 (en) | 2013-08-07 |
CN102959184B (zh) | 2015-11-25 |
CN102959184A (zh) | 2013-03-06 |
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